Piston engine assembly

ABSTRACT

A variable compression piston assembly includes a plurality of pistons, a transition arm coupled to each of the pistons, and a rotating member mounted for pivoting movement to slide along an axis of the drive member. Movement of the rotating member relative to the drive member changes the compression ratio of the piston assembly. An engine assembly includes first and second piston assemblies mounted back-to-back and 180° out of phase. A joint for positioning between first and second pistons includes an outer member and an inner member. The outer member is configured for movement relative to the pistons along a first axis perpendicular to the common axis of the pistons. The inner member is mounted within the outer member for rotation relative to the outer member about a second axis perpendicular to the first axis and the common axis.

This application is a continuation of application Ser. No. 09/276,314filed, Mar. 25, 1999, entitled PISTON ENGINE ASSEMBLY, which is acontinuation-in-part of application Ser. No. 09/154,153, filed Sep. 15,1998, entitled VARIABLE COMPRESSION PISTON ASSEMBLY, now abandoned,which is a continuation-in-part of application Ser. No. 08/929,042,filed Sep. 15, 1997, entitled DOUBLE ENDED PISTON ENGINE, now U.S. Pat.No. 6,019,073.

BACKGROUND OF THE INVENTION

The invention relates to a variable compression piston assembly, and toan engine that has double ended pistons connected to a universal jointfor converting linear motion of the pistons to rotary motion.

Most piston driven engines have pistons that are attached to offsetportions of a crankshaft such that as the pistons are moved in areciprocal direction transverse to the axis of the crankshaft, thecrankshaft will rotate.

U.S. Pat. No. 5,535,709, defines an engine with a double ended pistonthat is attached to a crankshaft with an off set portion. A leverattached between the piston and the crankshaft is restrained in afulcrum regulator to provide the rotating motion to the crankshaft.

U.S. Pat. No. 4,011,842, defines a four cylinder piston engine thatutilizes two double ended pistons connected to a T-shaped T-shapedconnecting member that causes a crankshaft to rotate. The T-shapedconnecting member is attached at each of the T-cross arm to a doubleended piston. A centrally located point on the T-cross arm is rotatablyattached to a fixed point, and the bottom of the T is rotatably attachedto a crank pin which is connected to the crankshaft by a crankthrowwhich includes a counter weight.

In each of the above examples, double ended pistons are used that drivea crankshaft that has an axis transverse to the axis of the pistons.

SUMMARY OF THE INVENTION

According to the invention, a variable compression piston assemblyincludes a plurality of pistons, a transition arm coupled to each of thepistons, and a rotating member coupled to a drive member of thetransition arm and mounted for pivoting movement to slide along an axisof the drive member. Movement of the rotating member relative to thedrive member changes the compression ratio of the piston assembly.

Embodiments of this aspect of the invention may include one or more ofthe following features.

The pistons are double ended pistons. The transition arm is coupled toeach of the double ended pistons at approximately a center of eachdouble ended piston. There are two pistons and the axis of rotation ofthe rotating member and axes of the two pistons lie on a common plane.

In certain illustrated embodiments, the rotating member is a flywheel. Acounterweight is mounted to the rotating member. The rotating member ispivotably mounted to a main drive shaft. The axis of the main driveshaft is parallel to the axis of each of the pistons.

A movable pressure plate is in contact with a peripheral region of therotating member. A roller interfaces the pressure plate and the rotatingmember. A piston biases the rotating member into contact with thepressure plate.

The drive member extends into an opening in the rotatable memberadjacent to a periphery of the rotatable member. The drive arm extendsinto a pivot pin located in the rotatable member. A universal jointconnects the transition arm to a support.

According to another aspect of the invention, a method for varying thecompression ratio of a piston assembly includes providing a plurality ofpistons, a transition arm coupled to each of the pistons, and a rotatingmember coupled to a drive member of the transition arm and mounted forpivoting movement to slide along an axis of the drive member. The methodincludes pivoting the rotating member to change the compression ratio ofthe piston assembly.

According to another aspect of the invention, a method of increasing theefficiency of a piston assembly includes providing a plurality of doubleended pistons, a transition arm coupled to each of the double endedpistons at approximately a center of each of the pistons, and a rotatingmember coupled to a drive member of the transition arm and mounted forpivoting movement to slide along an axis of the drive member. The methodincludes pivoting the rotating member to change the compression ratio ofthe double ended piston assembly.

According to another aspect of the invention, a joint for positioningbetween first and second elements arranged for linear motion along acommon axis includes an outer member and an inner member. The outermember is configured for movement relative to the first and secondelements along a first axis perpendicular to the common axis. The innermember is mounted within the outer member for rotation relative to theouter member about a second axis perpendicular to the first axis and thecommon axis. The outer and inner members each define an opening forreceiving a drive arm.

Embodiments of this aspect of the invention may include one or more ofthe following features.

The outer member is configured for movement relative to the first andsecond elements along the second axis. The outer member defines firstand second parallel flat sides each defining a plane perpendicular tothe common axis. First and second sliding members are positioned betweenthe first flat side and the first element and the second flat side andthe second element, respectively. The flat sides have a polishedsurface.

The first and second elements are pistons. Alternatively, the firstelement is a piston and the second element is a guided rod, e.g., of acompressor.

The drive arm defines a longitudinal axis and the joint includes amount, e.g., a cap screw, for holding the drive arm axially stationarywhile permitting the drive arm to rotate about its longitudinal axis.

In an illustrated embodiment, the opening in the inner member forreceiving the drive arm is a channel defining a channel axisperpendicular to the second axis. The opening in the outer member forreceiving the drive arm is a slot for accommodating movement of thedrive arm when the inner member rotates relative to outer member.

A thrust bearing receives an axial load transferred to the drive arm bythe first and second elements. A sleeve bearing receives a normal loadtransferred to the drive arm by the first and second elements. There isalso a bearing located between the inner and outer members.

The first and second elements are mounted to a connector and theconnector defines a cavity within which the outer and inner members arepositioned.

According to another aspect of the invention, a piston assembly includesfirst and second elements configured for linear motion along a commonaxis and a joint positioned between the first and second elements. Atleast one of the first and second elements is a piston.

According to another aspect of the invention, a method of reducing sideload in a double ended member having first and second elements arrangedfor linear motion along an axis of the double ended member includesproviding a joint located between the first and second elements, andtransferring load between the first and second elements and a drive armmounted to the joint through two opposed surfaces, e.g., flat surfaces,of an outer member of the joint.

According to another aspect of the invention, an engine assemblyincludes a first piston assembly including at least two engine pistonscoupled by a transition arm, and a second piston assembly coupled to thefirst piston assembly. The second piston assembly including at least twoengine pistons coupled by a transition arm. The first and second pistonassemblies are mounted back-to-back and 180° out of phase.

Embodiments of this aspect of the invention may include one or more ofthe following features. The engine pistons are housed in cylinders withpairs of engine pistons from the first and second piston assembliessharing a common cylinder. Each piston assembly includes compressorpistons mounted to move with respective engine pistons. Each pistonassembly includes six pistons and two compressors.

In an illustrated embodiment, a first rotating member is mounted to thetransition arm of the first piston assembly, and a second rotatingmember is mounted to the transition arm of the second piston assembly.The second rotating member is coupled to the first rotating member.

According to another aspect of the invention, a method of cancellingvibration in an engine assembly includes providing a first pistonassembly including at least two engine pistons coupled by a transitionarm, providing a second piston assembly including at least two enginepistons coupled by a transition arm, and coupling the first and secondpiston assemblies in a back-to-back relationship and 180° out of phase.

BRIEF DESCRIPTION OF THE DRAWINGS

FIGS. 1 and 2 are side view of a simplified illustration of a fourcylinder engine of the present invention;

FIGS. 3, 3 a, 4, 4 a, 5, 5 a, and 6, 6 a are a top views of the engineof FIG. 1 showing the pistons and flywheel in four different positions;

FIG. 7 is a top view, partially in cross-section of an eight cylinderengine of the present invention;

FIG. 8 is a side view in cross-section of the engine of FIG. 7;

FIG. 9 is a right end view of FIG. 7;

FIG. 10 is a side view of FIG. 7;

FIG. 11 is a left end view of FIG. 7;

FIG. 12 is a partial top view of the engine of FIG. 7 showing thepistons, drive member and flywheel in a high compression position;

FIG. 13 is a partial top view of the engine in FIG. 7 showing thepistons, drive member and flywheel in a low compression position;

FIG. 14 is a top view of a piston;

FIG. 15 is a side view of a piston showing the drive member in twopositions;

FIG. 16 shows the bearing interface of the drive member and the piston;

FIG. 17 is an air driven engine/pump embodiment;

FIG. 18 illustrates the air valve in a first position;

FIGS. 18a, 18 b and 18 c are cross-sectional view of threecross-sections of the air valve shown in FIG. 18;

FIG. 19 illustrates the air valve in a second position;

FIGS. 19a, 19 b and 19 c are cross-sectional view of threecross-sections for the air valve shown in FIG. 19;

FIG. 20 shows an embodiment with slanted cylinders;

FIG. 21 shows an embodiment with single ended pistons;

FIG. 22 is a top view of a two cylinder, double ended piston assembly;

FIG. 23 is a top view of one of the double ended pistons of the assemblyof FIG. 22;

FIG. 23a is a side view of the double ended piston of FIG. 23, takenalong lines 23A, 23A;

FIG. 24 is a top view of a transition arm and universal joint of thepiston assembly of FIG. 22;

FIG. 24a is a side view of the transition arm and universal joint ofFIG. 24, taken along lines 24 a, 24 a;

FIG. 25 is a perspective view of a drive arm connected to the transitionarm of the piston assembly of FIG. 22;

FIG. 25a is an end view of a rotatable member of the piston assembly ofFIG. 22, taken along lines 25 a, 25 a of FIG. 22, and showing theconnection of the drive arm to the rotatable member;

FIG. 25b is a side view of the rotatable member, taken along lines 25 b,25 b of FIG. 25a;

FIG. 26 is a cross-sectional, top view of the piston assembly of FIG.22;

FIG. 27 is an end view of the transition arm, taken along lines 27, 27of FIG. 24;

FIG. 27a is a cross-sectional view of a drive pin of the piston assemblyof FIG. 22;

FIGS. 28-28b are top, rear, and side views, respectively, of the pistonassembly of FIG. 22;

FIG. 28c is a top view of an auxiliary shaft of the piston assembly ofFIG. 22;

FIG. 29 is a cross-sectional side view of a zero-stroke coupling;

FIG. 29a is an exploded view of the zero-stroke coupling of FIG. 29;

FIG. 30 is a graph showing the FIG. 8 motion of a non-flat pistonassembly;

FIG. 31 shows a reinforced drive pin;

FIG. 32 is a top view of a four cylinder engine for directly applyingcombustion pressures to pump pistons;

FIG. 32a is an end view of the four cylinder engine, taken along lines32 a, 32 a of FIG. 32;

FIG. 33 is a cross-sectional top view of an alternative embodiment of avariable stroke assembly shown in a maximum stroke position;

FIG. 34 is a cross-sectional top view of the embodiment of FIG. 33 shownin a minimum stroke position;

FIG. 35 is a partial, cross-sectional top view of an alternativeembodiment of a double-ended piston joint;

FIG. 35A is an end view and

FIG. 35B is a side view of the double-ended piston joint, taken alonglines 35A, 35A and 35B, 35B, respectively, of FIG. 35;

FIG. 36 is a partial, cross-sectional top view of the double-endedpiston joint of FIG. 35 shown in a rotated position;

FIG. 37 is a side view of an alternative embodiment of the joint of FIG.35;

FIG. 38 is a top view of an engine/compressor assembly; and

FIG. 38A is an end view and

FIG. 38B is a side view of the engine/compressor assembly, taken alonglines 38A, 38A and 38B, 38B, respectively, of FIG. 38.

DESCRIPTION OF THE PREFERRED EMBODIMENTS

FIG. 1 is a pictorial representation of a four piston engine 10 of thepresent invention. Engine 10 has two cylinders 11 (FIG. 3) and 12. Eachcylinder 11 and 12 house a double ended piston. Each double ended pistonis connected to transition arm 13 which is connected to flywheel 15 byshaft 14. Transition arm 13 is connected to support 19 by a universaljoint mechanism, including shaft 18, which allows transition arm 13 tomove up an down and shaft 17 which allows transition arm 13 to move sideto side. FIG. 1 shows flywheel 15 in a position shaft 14 at the top ofwheel 15.

FIG. 2 shows engine 10 with flywheel 15 rotated so that shaft 14 is atthe bottom of flywheel 15. Transition arm 13 has pivoted downward onshaft 18.

FIGS. 3-6 show a top view of the pictorial representation, showing thetransition arm 13 in four positions and shaft moving flywheel 15 in 900°increments. FIG. 3 shows flywheel 15 with shaft 14 in the position asillustrated in FIG. 3a. When piston 1 fires and moves toward the middleof cylinder 11, transition arm 13 will pivot on universal joint 16rotating flywheel 15 to the position shown in FIG. 2. Shaft 14 will bein the position shown in FIG. 4a. When piston 4 is fired, transition arm13 will move to the position shown in FIG. 5. Flywheel 15 and shaft 14will be in the position shown in FIG 5 a. Next piston 2 will fire andtransition arm 13 will be moved to the position shown in FIG. 6.Flywheel 15 and shaft 14 will be in the position shown in FIG. 6a. Whenpiston 3 is fired, transition arm 13 and flywheel 15 will return to theoriginal position that shown in FIGS. 3 and 3a.

When the pistons fire, transition arm will be moved back and forth withthe movement of the pistons. Since transition arm 13 is connected touniversal joint 16 and to flywheel 15 through shaft 14, flywheel 15rotates translating the linear motion of the pistons to a rotationalmotion.

FIG. 7 shows (in partial cross-section) a top view of an embodiment of afour double piston, eight cylinder engine 30 according to the presentinvention. There are actually only four cylinders, but with a doublepiston in each cylinder, the engine is equivalent to a eight cylinderengine. Two cylinders 31 and 46 are shown. Cylinder 31 has double endedpiston 32, 33 with piston rings 32 a and 33 a, respectively. Pistons 32,33 are connected to a transition arm 60 (FIG. 8) by piston arm 54 aextending into opening 55 a in piston 32, 33 and sleeve bearing 55.Similarly piston 47, 49, in cylinder 46 is connected by piston arm 54 bto transition arm 60.

Each end of cylinder 31 has inlet and outlet valves controlled by arocker arms and a spark plug. Piston end 32 has rocker arms 35 a and 35b and spark plug 44, and piston end 33 has rocker arms 34 a and 34 b,and spark plug 41. Each piston has associated with it a set of valves,rocker arms and a spark plug. Timing for firing the spark plugs andopening and closing the inlet and exhaust values is controlled by atiming belt 51 which is connected to pulley 50 a. Pulley 50 a isattached to a gear 64 by shaft 63 (FIG. 8) turned by output shaft 53powered by flywheel 69. Belt 50 a also turns pulley 50 b and gear 39connected to distributor 38. Gear 39 also turns gear 40. Gears 39 and 40are attached to cam shaft 75 (FIG. 8) which in turn activate push rodsthat are attached to the rocker arms 34, 35 and other rocker arms notillustrated.

Exhaust manifolds 48 and 56 as shown attached to cylinders 46 and 31respectively. Each exhaust manifold is attached to four exhaust ports.

FIG. 8 is a side view of engine 30, with one side removed, and takenthrough section 8—8 of FIG. 7. Transitions arm 60 is mounted on support70 by pin 72 which allows transition arm to move up and down (as viewedin FIG. 8) and pin 71 which allows transition arm 60 to move from sideto side. Since transition arm 60 can move up and down while moving sideto side, then shaft 61 can drive flywheel 69 in a circular path. Thefour connecting piston arms (piston arms 54 b and 54 d shown in FIG. 8)are driven by the four double end pistons in an oscillator motion aroundpin 71. The end of shaft 61 in flywheel 69 causes transition arm to moveup and down as the connection arms move back and forth. Flywheel 69 hasgear teeth 69 a around one side which may be used for turning theflywheel with a starter motor 100 (FIG. 11) to start the engine.

The rotation of flywheel 69 and drive shaft 68 connected thereto, turnsgear 65 which in turn turns gears 64 and 66. Gear 64 is attached toshaft 63 which turns pulley 50 a. Pulley 50 a is attached to belt 51.Belt 51 turns pulley 50 b and gears 39 and 40 (FIG. 7). Cam shaft 75 hascams 88-91 on one end and cams 84-87 on the other end. Cams 88 and 90actuate push rods 76 and 77, respectively. Cams 89 and 91 actuate pushrods 93 and 94, respectively. Cams 84 and 86 actuate push rods 95 and96, respectively, and cams 85 and 87 actuate push rods 78 and 79,respectively. Push rods 77, 76, 93, 94, 95, 96 and 78, 79 are foropening and closing the intake and exhaust valves of the cylinders abovethe pistons. The left side of the engine, which has been cutaway,contains an identical, but opposite valve drive mechanism.

Gear 66 turned by gear 65 on drive shaft 68 turns pump 67, which may be,for example, a water pump used in the engine cooling system (notillustrated), or an oil pump.

FIG. 9 is a rear view of engine 30 showing the relative positions of thecylinders and double ended pistons. Piston 32, 33 is shown in dashedlines with valves 35 c and 35 d located under lifter arms 35 a and 35 b,respectively. Belt 51 and pulley 50 b are shown under distributor 38.Transition arm 60 and two, 54 c and 54 d, of the four piston arms 54 a,54 b, 54 c and 54 d are shown in the pistons 32-33, 32 a-33 a, 47-49 and47 a-49 a.

FIG. 10 is a side view of engine 30 showing the exhaust manifold 56,intake manifold 56 a and carburetor 56 c. Pulleys 50 a and 50 b withtiming belt 51 are also shown.

FIG. 11 is a front end view of engine 30 showing the relative positionsof the cylinders and double ended pistons 32-33, 32 a-33 a, 47-49 and 47a-49 a with the four piston arms 54 a, 54 b, 54 c and 54 d positioned inthe pistons. Pump 67 is shown below shaft 53, and pulley 50 a and timingbelt 51 are shown at the top of engine 30. Starter 100 is shown withgear 101 engaging the gear teeth 69 a on flywheel 69.

A feature of the invention is that the compression ratio for the enginecan be changed while the engine is running. The end of arm 61 mounted inflywheel 69 travels in a circle at the point where arm 61 entersflywheel 69. Referring to FIG. 13, the end of arm 61 is in a sleevebearing ball bushing assembly 81. The stroke of the pistons iscontrolled by arm 61. Arm 61 forms an angle, for example about 15°, withshaft 53. By moving flywheel 69 on shaft 53 to the right or left, asviewed in FIG. 13, the angle of arm 61 can be changed, changing thestroke of the pistons, changing the compression ratio. The position offlywheel 69 is changed by turning nut 104 on threads 105. Nut 104 iskeyed to shaft 53 by thrust bearing 106 a held in place by ring 106 b.In the position shown in FIG. 12, flywheel 69 has been moved to theright, extending the stroke of the pistons.

FIG. 12 shows flywheel moved to the right increasing the stroke of thepistons, providing a higher compression ratio. Nut 105 has been screwedto the right, moving shaft 53 and flywheel 69 to the right. Arm 61extends further into bushing assembly 80 and out the back of flywheel69.

FIG. 13 shows flywheel moved to the left reducing the stroke of thepistons, providing a lower compression ratio. Nut 105 has been screwedto the left, moving shaft 53 and flywheel 69 to the left. Arm 61 extendsless into bushing assembly 80.

The piston arms on the transition arm are inserted into sleeve bearingsin a bushing in piston. FIG. 14 shows a double piston 110 having pistonrings 111 on one end of the double piston and piston rings 112 on theother end of the double piston. A slot 113 is in the side of the piston.The location the sleeve bearing is shown at 114.

FIG. 15 shows a piston arm 116 extending into piston 110 through slot116 into sleeve bearing 117 in bushing 115. Piston arm 116 is shown in asecond position at 116 a. The two pistons arms 116 and 116 a show themovement limits of piston arm 116 during operation of the engine.

FIG. 16 shows piston arm 116 in sleeve bearing 117. Sleeve bearing 117is in pivot pin 115. Piston arm 116 can freely rotate in sleeve bearing117 and the assembly of piston arm 116, Sleeve bearing 117 and pivot pin115 and sleeve bearings 118 a and 118 b rotate in piston 110, and pistonarm 116 can moved axially with the axis of sleeve bearing 117 to allowfor the linear motion of double ended piston 110, and the motion of atransition arm to which piston arm 116 is attached.

FIG. 17 shows how the four cylinder engine 10 in FIG. 1 may beconfigured as an air motor using a four way rotary valve 123 on theoutput shaft 122. Each of cylinders 1, 2, 3 and 4 are connected by hoses131. 132, 133, and 144, respectively, to rotary valve 123. Air inletport 124 is used to supply air to run engine 120. Air is sequentiallysupplied to each of the pistons 1 a, 2 a, 3 a and 4 a, to move thepistons back and forth in the cylinders. Air is exhausted from thecylinders out exhaust port 136. Transition arm 126, attached to thepistons by connecting pins 127 and 128 are moved as described withreferences to FIGS. 1-6 to turn flywheel 129 and output shaft 22.

FIG. 18 is a cross-sectional view of rotary valve 123 in the positionwhen pressurized air or gas is being applied to cylinder 1 through inletport 124, annular channel 125, channel 126, channel 130, and air hose131. Rotary valve 123 is made up of a plurality of channels in housing123 and output shaft 122. The pressurized air entering cylinder 1 causespiston 1 a, 3 a to move to the right (as viewed in FIG. 18). Exhaust airis forced out of cylinder 3 through line 133 into chamber 134, throughpassageway 135 and out exhaust outlet 136.

FIGS. 18a, 18 b and 18 c are cross-sectional view of valve 23 showingthe air passages of the valves at three positions along valve 23 whenpositioned as shown in FIG. 18.

FIG. 19 shows rotary valve 123 rotated 180° when pressurized air isapplied to cylinder 3, reversing the direction of piston 1 a, 3 a.Pressurized air is applied to inlet port 124, through annular chamber125, passage way 126, chamber 134 and air line 133 to cylinder 3. Thisin turn causes air in cylinder 1 to be exhausted through line 131,chamber 130, line 135, annular chamber 137 and out exhaust port 136.Shaft 122 will have rotated 360° turning counter clockwise when piston 1a, 3 a complete it stroke to the left.

Only piston 1 a, 3 a have been illustrated to show the operation of theair engine and valve 123 relative to the piston motion. The operation ofpiston 2 a, 4 a is identical in function except that its 360° cyclestarts at 90° shaft rotation and reverses at 270° and completes itscycle back at 90°. A power stroke occurs at every 90° of rotation.

FIGS. 19a, 19 b and 19 c are cross-sectional views of valve 123 showingthe air passages of the valves at three positions along valve 123 whenpositioned as shown in FIG. 19.

The principle of operation which operates the air engine of FIG. 17 canbe reversed, and engine 120 of FIG. 17 can be used as an air or gascompressor or pump. By rotating engine 10 clockwise by applying rotarypower to shaft 122, exhaust port 136 will draw in air into the cylindersand port 124 will supply air which may be used to drive, for example airtool, or be stored in an air tank.

In the above embodiments, the cylinders have been illustrated as beingparallel to each other. However, the cylinders need not be parallel.FIG. 20 shows an embodiment similar to the embodiment of FIGS. 1-6, withcylinders 150 and 151 not parallel to each other. Universal joint 160permits the piston arms 152 and 153 to be at an angle other than 90° tothe drive arm 154. Even with the cylinders not parallel to each otherthe engines are functionally the same.

Still another modification may be made to the engine 10 of FIGS. 1-6.This embodiment, pictorially shown in FIG. 21, may have single endedpistons. Piston 1 a and 2 a are connected to universal joint 170 bydrive arms 171 and 172, and to flywheel 173 by drive arm 174. The basicdifference is the number of strokes of pistons 1 a and 2 a to rotateflywheel 173 360°.

Referring to FIG. 22, a two cylinder piston assembly 300 includescylinders 302, 304, each housing a variable stroke, double ended piston306, 308, respectively. Piston assembly 300 provides the same number ofpower strokes per revolution as a conventional four cylinder engine.Each double ended piston 306, 308 is connected to a transition arm 310by a drive pin 312, 314, respectively. Transition arm 310 is mounted toa support 316 by, e.g., a universal joint 318 (U-joint), constantvelocity joint, or spherical bearing. A drive arm 320 extending fromtransition arm 310 is connected to a rotatable member, e.g., flywheel322.

Transition arm 310 transmits linear motion of pistons 306, 308 to rotarymotion of flywheel 322. The axis, A, of flywheel 322 is parallel to theaxes, B and C, of pistons 306, 308 (though axis, A, could be off-axis asshown in FIG. 20) to form an axial or barrel type engine, pump, orcompressor. U-joint 318 is centered on axis, A. As shown in FIG. 28α,pistons 306, 308 are 180° apart with axes A, B and C lying along acommon plane, D, to form a flat piston assembly.

Referring to FIGS. 22 and 23, cylinders 302, 304 each include left andright cylinder halves 301 a, 301 b mounted to the assembly casestructure 303. Double ended pistons 306, 308 each include two pistons330 and 332, 330 a and 332 a, respectively, joined by a central joint334, 334 a, respectively. The pistons are shown having equal length,though other lengths are contemplated. For example, joint 334 can beoff-center such that piston 330 is longer than piston 332. As thepistons are fired in sequence 330 a, 332, 330, 332 a, from the positionshown in FIG. 22, flywheel 322 is rotated in a clockwise direction, asviewed in the direction of arrow 333. Piston assembly 300 is a fourstroke cycle engine, i.e., each piston fires once in two revolutions offlywheel 322.

As the pistons move back and forth, drive pins 312, 314 must be free torotate about their common axis, E, (arrow 305), slide along axis, E,(arrow 307) as the radial distance to the center line, B, of the pistonchanges with the angle of swing, a, of transition arm 310 (approximately±15° swing), and pivot about centers, F, (arrow 309). Joint 334 isconstructed to provide this freedom of motion.

Joint 334 defines a slot 340 (FIG. 23a) for receiving drive pin 312, anda hole 336 perpendicular to slot 340 housing a sleeve bearing 338. Acylinder 341 is positioned within sleeve bearing 338 for rotation withinthe sleeve bearing. Sleeve bearing 338 defines a side slot 342 shapedlike slot 340 and aligned with slot 340. Cylinder 341 defines a throughhole 344. Drive pin 312 is received within slot 342 and hole 344. Anadditional sleeve bearing 346 is located in through hole 344 of cylinder341. The combination of slots 340 and 342 and sleeve bearing 338 permitdrive pin 312 to move along arrow 309. Sleeve bearing 346 permits drivepin 312 to rotate about its axis, E, and slide along its axis, E.

If the two cylinders of the piston assembly are configured other than180° apart, or more than two cylinders are employed, movement ofcylinder 341 in sleeve bearing 338 along the direction of arrow 350allows for the additional freedom of motion required to prevent bindingof the pistons as they undergo a FIG. 8 motion, discussed below. Slot340 must also be sized to provide enough clearance to allow the FIG. 8motion of the pin.

Referring to FIGS. 35-35B, an alternative embodiment of a central joint934 for joining pistons 330 and 332 is configured to produce zero sideload on pistons 330 and 332. Joint 934 permits the four degrees offreedom necessary to prevent binding of drive pin 312 as the pistonsmove back and forth, i.e., rotation about axis, E, (arrow 905), pivotingabout center, F, (arrow 909), and sliding movement along orthogonalaxes, M (up and down in the plane of the paper in FIG. 35) and N (in andout of the plane of the paper in FIG. 35), while the load transmittedbetween joint 934 and pistons 330, 332 only produces a force vectorwhich is parallel to piston axis, B (which is orthogonal to axes M andN).

Sliding movement along axis, M, accommodates the change in the radialdistance of transition arm 310 to the center line, B, of the piston withthe angle of swing, α, of transition arm 310. Sliding movement alongaxis, N, allows for the additional freedom of motion required to preventbinding of the pistons as they undergo the figure eight motion,discussed below. Joint 934 defines two opposed flat faces 937, 937 awhich slide in the directions of axes M and N relative to pistons 330,332. Faces 937, 937 a define parallel planes which remain perpendicularto piston axis, B, during the back and forth movement of the pistons.

Joint 934 includes an outer slider member 935 which defines faces 937,937 a for receiving the driving force from pistons 330, 332. Slidermember 935 defines a slot 940 in a third face 945 of the slider forreceiving drive pin 312, and a slot 940 a in a fourth face 945 a. Slidermember 935 has an inner wall 936 defining a hole 939 perpendicular toslot 940 and housing a slider sleeve bearing 938. A cross shaft 941 ispositioned within sleeve bearing 938 for rotation within the sleevebearing in the direction of arrow 909. Sleeve bearing 938 defines a sideslot 942 shaped like slot 940 and aligned with slot 940. Cross shaft 941defines a through hole 944. Drive pin 312 is received within slot 942and hole 944. A sleeve bearing 946 is located in through hole 944 ofcross shaft 941.

The combination of slots 940 and 942 and sleeve bearing 938 permit drivepin 312 to move in the direction of arrow 909. Positioned within slot940 a is a cap screw 947 and washer 949 which attach to drive pin 312retaining drive pin 312 against a step 951 defined by cross shaft 941while permitting drive pin 312 to rotate about its axis, E, andpreventing drive pin 312 from sliding along axis, E. As discussed above,the two addition freedoms of motion are provided by sliding of sliderfaces 937, 937 a relative to pistons 330, 332 along axis, M and N. Aplate 960 is placed between each of face 937 and piston 330 and face 937a and piston 332. Each plate 960 is formed of a low friction bearingmaterial with a bearing surface 962 in contact with faces 937, 937 a,respectively. Faces 937, 937 a are polished.

As shown in FIG. 36, the load, P_(L), applied to joint 934 by piston 330in the direction of piston axis, B, is resolved into two perpendicularloads acting on pin 312: axial load, A_(L), along the axis, E, of drivepin 312, and normal load, N_(L), perpendicular to drive pin axis, E. Theaxial load is applied to thrust bearings 950, 952, and the normal loadis applied to sleeve bearing 946. The net direction of the forcestransmitted between pistons 330, 332 and joint 934 remains along pistonaxis, B, preventing side loads being applied to pistons 330, 332. Thisis advantageous because side loads on pistons 330, 332 can cause thepistons to contact the cylinder wall creating frictional lossesproportional to the side load values.

Pistons 330, 332 are mounted to joint 934 by a center piece connector970. Center piece 970 includes threaded ends 972, 974 for receivingthreaded ends 330 a and 332 a of the pistons, respectively. Center piece970 defines a cavity 975 for receiving joint 934. A gap 976 is providedbetween joint 934 and center piece 970 to permit motion along axis, N.

For an engine capable of producing, e.g., about 100 horsepower, joint934 has a width, W, of, e.g., about 3{fraction (5/16)} inches, a length,L₁, of, e.g., 3{fraction (5/16)} inches, and a height, H, of, e.g.,about 3½ inches. The joint and piston ends together have an overalllength, L₂, of, e.g., about 9{fraction (5/16)} inches, and a diameter,D₁, of, e.g., about 4 inches. Plates 960 have a diameter, D₂, of, e.g.,about 3¼ inch, and a thickness, T, of, e.g., about ⅛ inch. Plates 960are press fit into the pistons. Plates 960 are preferably bronze, andslider 935 is preferably steel or aluminum with a steel surface definingfaces 937, 937 a.

Joint 934 need not be used to join two pistons. One of pistons 330, 332can be replaced by a rod guided in a bushing.

Where figure eight motion is not required or is allowed by motion ofdrive pin 312 within cross shaft 941, joint 934 need not slide in thedirection of axis, N. Referring to FIG. 37, slider member 935 a andplates 960 a have curved surfaces permitting slider member 935 a toslide in the direction of axis, M, (in and out of the paper in FIG. 37)while preventing slider member 935 a to move along axis, N.

Referring to FIGS. 24 and 24a, U-joint 318 defines a central pivot 352(drive pin axis, E, passes through center 352), and includes a verticalpin 354 and a horizontal pin 356. Transition arm 310 is capable ofpivoting about pin 354 along arrow 358, and about pin 356 along arrow360.

Referring to FIGS. 25, 25 a and 25 b, as an alternative to a sphericalbearing, to couple transition arm 310 to flywheel 322, drive arm 320 isreceived within a cylindrical pivot pin 370 mounted to the flywheeloffset radially from the center 372 of the flywheel by an amount, e.g.,2.125 inches, required to produce the desired swing angle, α (FIG. 22),in the transition arm.

Pivot pin 370 has a through hole 374 for receiving drive arm 320. Thereis a sleeve bearing 376 in hole 374 to provide a bearing surface fordrive arm 320. Pivot pin 370 has cylindrical extensions 378, 380positioned within sleeve bearings 382, 384, respectively. As theflywheel is moved axially along drive arm 320 to vary the swing angle,α, and thus the compression ratio of the assembly, as described furtherbelow, pivot pin 370 rotates within sleeve bearings 382, 384 to remainaligned with drive arm 320. Torsional forces are transmitted throughthrust bearings 388, 390, with one or the other of the thrust bearingscarrying the load depending on the direction of the rotation of theflywheel along arrow 386.

Referring to FIG. 26, to vary the compression and displacement of pistonassembly 300, the axial position of flywheel 322 along axis, A, isvaried by rotating a shaft 400. A sprocket 410 is mounted to shaft 400to rotate with shaft 400. A second sprocket 412 is connected to sprocket410 by a roller chain 413. Sprocket 412 is mounted to a threadedrotating barrel 414. Threads 416 of barrel 414 contact threads 418 of astationary outer barrel 420.

Rotation of shaft 400, arrow 401, and thus sprockets 410 and 412, causesrotation of barrel 414. Because outer barrel 420 is fixed, the rotationof barrel 414 causes barrel 414 to move linearly along axis, A, arrow403. Barrel 414 is positioned between a collar 422 and a gear 424, bothfixed to a main drive shaft 408. Drive shaft 408 is in turn fixed toflywheel 322. Thus, movement of barrel 414 along axis, A, is translatedto linear movement of flywheel 322 along axis, A. This results inflywheel 322 sliding along axis, H, of drive arm 320 of transition arm310, changing angle, β, and thus the stroke of the pistons. Thrustbearings 430 are located at both ends of barrel 414, and a sleevebearing 432 is located between barrel 414 and shaft 408.

To maintain the alignment of sprockets 410 and 412, shaft 400 isthreaded at region 402 and is received within a threaded hole 404 of across bar 406 of assembly case structure 303. The ratio of the number ofteeth of sprocket 412 to sprocket 410 is, e.g., 4:1. Therefore, shaft400 must turn four revolutions for a single revolution of barrel 414. Tomaintain alignment, threaded region 402 must have four times the threadsper inch of barrel threads 416, e.g., threaded region 402 has thirty-twothreads per inch, and barrel threads 416 have eight threads per inch.

As the flywheel moves to the right, as viewed in FIG. 26, the stroke ofthe pistons, and thus the compression ratio, is increased. Moving theflywheel to the left decreases the stroke and the compression ratio. Afurther benefit of the change in stroke is a change in the displacementof each piston and therefore the displacement of the engine. Thehorsepower of an internal combustion engine closely relates to thedisplacement of the engine. For example, in the two cylinder, flatengine, the displacement increases by about 20% when the compressionratio is raised from 6:1 to 12:1. This produces approximately 20% morehorsepower due alone to the increase in displacement. The increase incompression ratio also increases the horsepower at the rate of about 5%per point or approximately 25% in horsepower. If the horsepower weremaintained constant and the compression ratio increased from 6:1 to12:1, there would be a reduction in fuel consumption of approximately25%.

The flywheel has sufficient strength to withstand the large centrifugalforces seen when assembly 300 is functioning as an engine. The flywheelposition, and thus the compression ratio of the piston assembly, can bevaried while the piston assembly is running.

Piston assembly 300 includes a pressure lubrication system. The pressureis provided by an engine driven positive displacement pump (not shown)having a pressure relief valve to prevent overpressures. Bearings 430and 432 of drive shaft 408 and the interface of drive arm 320 withflywheel 322 are lubricated via ports 433 (FIG. 26).

Referring to FIG. 27, to lubricate U-joint 318, piston pin joints 306,308, and the cylinder walls, oil under pressure from the oil pump isported through the fixed U-joint bracket to the top and bottom ends ofthe vertical pivot pin 354. Oil ports 450, 452 lead from the verticalpin to openings 454, 456, respectively, in the transition arm. As shownin FIG. 27A, pins 312, 314 each define a through bore 458. Each throughbore 458 is in fluid communication with a respective one of openings454, 456. As shown in FIG. 23, holes 460, 462 in each pin connectthrough slots 461 and ports 463 through sleeve bearing 338 to a chamber465 in each piston. Several oil lines 464 feed out from these chambersand are connected to the skirt 466 of each piston to provide lubricationto the cylinders walls and the piston rings 467. Also leading fromchamber 465 is an orifice to squirt oil directly onto the inside of thetop of each piston for cooling.

Referring to FIGS. 28-28c, in which assembly 300 is shown configured foruse as an aircraft engine 300 a, the engine ignition includes twomagnetos 600 to fire the piston spark plugs (not shown). Magnetos 600and a starter 602 are driven by drive gears 604 and 606 (FIG. 28c),respectively, located on a lower shaft 608 mounted parallel and belowthe main drive shaft 408. Shaft 608 extends the full length of theengine and is driven by gear 424 (FIG. 26) of drive shaft 408 and isgeared with a one to one ratio to drive shaft 408. The gearing for themagnetos reduces their speed to half the speed of shaft 608. Starter 602is geared to provide sufficient torque to start the engine.

Camshafts 610 operate piston push rods 612 through lifters 613.Camshafts 610 are geared down 2 to 1 through bevel gears 614, 616 alsodriven from shaft 608. Center 617 of gears 614, 616 is preferablyaligned with U-joint center 352 such that the camshafts are centered inthe piston cylinders, though other configurations are contemplated. Asingle carburetor 620 is located under the center of the engine withfour induction pipes 622 routed to each of the four cylinder intakevalves (not shown). The cylinder exhaust valves (not shown) exhaust intotwo manifolds 624.

Engine 300 a has a length, L, e.g., of about forty inches, a width, W,e.g., of about twenty-one inches, and a height, H, e.g., of about twentyinches, (excluding support 303).

Referring to FIGS. 29 and 29a, a variable compression compressor or pumphaving zero stroke capability is illustrated. Here, flywheel 322 isreplaced by a rotating assembly 500. Assembly 500 includes a hollowshaft 502 and a pivot arm 504 pivotally connected by a pin 506 to a hub508 of shaft 502. Hub 508 defines a hole 510 and pivot arm 504 defines ahole 512 for receiving pin 506. A control rod 514 is located withinshaft 502. Control rod 514 includes a link 516 pivotally connected tothe remainder of rod 514 by a pin 518. Rod 514 defines a hole 511 andlink 516 defines a hole 513 for receiving pin 518. Control rod 514 issupported for movement along its axis, Z, by two sleeve bearings 520.7ink 516 and pivot arm 514 are connected by a pin 522. Link 516 definesa hole 523 and pivot arm 514 defines a hole 524 for receiving pin 522.

Cylindrical pivot pin 370 of FIG. 25 which receives drive arm 320 ispositioned within pivot arm 504. Pivot arm 504 defines holes 526 forreceiving cylindrical extensions 378, 380. Shaft 502 is supported forrotation by bearings 530, e.g., ball, sleeve, or roller bearings. Adrive, e.g, pulley 532 or gears, mounted to shaft 502 drives thecompressor or pump.

In operation, to set the desired stroke of the pistons, control rod 514is moved along its axis, M, in the direction of arrow 515, causing pivotarm 504 to pivot about pin 506, along arrow 517, such that pivot pin 370axis, N, is moved out of alignment with axis, M, (as shown in dashedlines) as pivot arm 504 slides-along the axis, H, (FIG. 26) of thetransition arm drive arm 320. When zero stroke of the pistons isdesired, axes M and N are aligned such that rotation of shaft 514 doesnot cause movement of the pistons. This configuration works for bothdouble ended and single sided pistons.

The ability to vary the piston stroke permits shaft 514 to be run at asingle speed by drive 532 while the output of the pump or compressor canbe continually varied as needed. When no output is needed, pivot arm 504simply spins around drive arm 320 of transition arm 310 with zero swingof the drive arm. When output is needed, shaft 514 is already running atfull speed so that when pivot arm 504 is pulled off-axis by control rod514, an immediate stroke is produced with no lag coming up to speed.There are therefore much lower stress loads on the drive system as thereare no start/stop actions. The ability to quickly reduce the stroke tozero provides protection from damage especially in liquid pumping when adownstream blockage occurs.

An alternative method of varying the compression and displacement of thepistons is shown in FIG. 33. The mechanism provides for varying of theposition of a counterweight attached to the flywheel to maintain systembalance as the stroke of the pistons is varied.

A flywheel 722 is pivotally mounted to an extension 706 of a main driveshaft 708 by a pin 712. By pivoting flywheel 722 in the direction ofarrow, Z, flywheel 722 slides along axis, H, of a drive arm 720 oftransition arm 710, changing angle, β (FIG. 26), and thus the stroke ofthe pistons. Pivoting flywheel 722 also causes a counterweight 714 tomove closer to or further from axis, A, thus maintaining near rotationalbalance.

To pivot flywheel 722, an axially and rotationally movable pressureplate 820 is provided. Pressure plate 820 is in contact with a roller822 rotationally mounted to counterweight 714 through a pin 824 andbearing 826. From the position shown in FIG. 33, a servo motor or handknob 830 turns a screw 832 which advances to move pressure plate 820 inthe direction of arrow, Y. This motion of pressure plate 820 causesflywheel 722 to pivot in the direction of arrow, Z, as shown in the FIG.34, to decrease the stroke of the pistons. Moving pressure plate 820 by0.75″ decreases the compression ratio from about 12:1 to about 6:1.

Pressure plate 820 is supported by three or more screws 832. Each screwhas a gear head 840 which interfaces with a gear 842 on pressure plate820 such that rotation of screw 832 causes rotation of pressure plate820 and thus rotation of the remaining screws to insure that thepressure plate is adequately supported. To ensure contact between roller822 and pressure plate 820, a piston 850 is provided which biasesflywheel 722 in the direction opposite to arrow, Z.

Referring to FIG. 30, if two cylinders not spaced 180° apart (as viewedfrom the end) or more than two cylinders are employed in piston assembly300, the ends of pins 312, 314 coupled to joints 306, 308 will undergo aFIG. 8 motion. FIG. 30 shows the FIG. 8 motion of a piston assemblyhaving four double ended pistons. Two of the pistons are arranged flatas shown in FIG. 22 (and do not undergo the FIG. 8 motion), and theother two pistons are arranged equally spaced between the flat pistons(and are thus positioned to undergo the largest FIG. 8 deviationpossible). The amount that the pins connected to the second set ofpistons deviate from a straight line (y axis of FIG. 30) is determinedby the swing angle (mast angle) of the drive arm and the distance thepin is from the central pivot point 352 (x axis of FIG. 30).

In a four cylinder version where the pins through the piston pivotassembly of each of the four double ended pistons are set at 45° fromthe axis of the central pivot, the figure eight motion is equal at eachpiston pin. Movement in the piston pivot bushing is provided where thefigure eight motion occurs to prevent binding.

When piston assembly 300 is configured for use, e.g., as a dieselengines, extra support can be provided at the attachment of pins 312,314 to transition arm 310 to account for the higher compression ofdiesel engines as compared to spark ignition engines. Referring to FIG.31, support 550 is bolted to transition arm 310 with bolts 551 andincludes an opening 552 for receiving end 554 of the pin.

Engines according to the invention can be used to directly applycombustion pressures to pump pistons. Referring to FIGS. 32 and 32a, afour cylinder, two stroke cycle engine 600 (each of the four pistons 602fires once in one revolution) applies combustion pressure to each offour pump pistons 604. Each pump piston 604 is attached to the outputside 606 of a corresponding piston cylinder 608. Pump pistons 604 extendinto a pump head 610.

A transition arm 620 is connected to each cylinder 608 and to a flywheel622, as described above. An auxiliary output shaft 624 is connected toflywheel 622 to rotate with the flywheel, also as described above.

The engine is a two stroke cycle engine because every stroke of a piston602 (as piston 602 travels to the right as viewed in FIG. 32) must be apower stroke. The number of engine cylinders is selected as required bythe pump. The pump can be a fluid or gas pump. In use as a multi-stageair compressor, each pump piston 606 can be a different diameter. Nobearing loads are generated by the pumping function (for single actingpump compressor cylinders), and therefore, no friction is introducedother than that generated by the pump pistons themselves.

Referring to FIGS. 38-38B, an engine 1010 having vibration cancellingcharacteristics and being particularly suited for use in gas compressionincludes two assemblies 1012, 1014 mounted back-to-back and 180° out ofphase. Engine 1010 includes a central engine section 1016 and outercompressor sections 1018, 1020. Engine section 1016 includes, e.g., sixdouble acting cylinders 1022, each housing a pair of piston 1024, 1026.A power stroke occurs when a center section 1028 of cylinder 1022 isfired, moving pistons 1024, 1026 away from each other. The opposedmovement of the pistons results in vibration cancelling.

Outer compression section 1018 includes two compressor cylinders 1030and outer compression section 1020 includes two compressor cylinders1032, though there could be up to six compressor cylinders in eachcompression section. Compression cylinders 1030 each house a compressionpiston 1034 mounted to one of pistons 1024 by a rod 1036, andcompression cylinders 1032 each house a compression piston 1038 mountedto one of pistons 1026 by a rod 1040. Compression cylinders 1030, 1032are mounted to opposite piston pairs such that the forces cancelminimizing vibration forces which would otherwise be transmitted intomounting 1041.

Pistons 1024 are coupled by a transition arm 1042, and pistons 1026 arecoupled by a transition arm 1044, as described above. Transition arm1042 includes a drive arm 1046 extending into a flywheel 1048, andtransition arm 1044 includes a drive arm 1050 extending into a flywheel1052, as described above. Flywheel 1048 is joined to flywheel 1052 by acoupling arm 1054 to rotate in synchronization therewith. Flywheels1048, 1052 are mounted on bearings 1056. Flywheel 1048 includes a bevelgear 1058 which drives a shaft 1060 for the engine starter, oil pump anddistributor for ignition, not shown.

Engine 1010 is, e.g., a two stroke natural gas engine having ports (notshown) in central section 1028 of cylinders 1022 and a turbocharger (notshown) which provides intake air under pressure for purging cylinders1022. Alternatively, engine 1010 is gasoline or diesel powered.

The stroke of pistons 1024, 1026 can be varied by moving both flywheels1048, 1052 such that the stroke of the engine pistons and the compressorpistons are adjusted equally reducing or increasing the engine power asthe pumping power requirement reduces or increases, respectively.

The vibration cancelling characteristics of the back-to-backrelationship of assemblies 1012, 1014 can be advantageously employed ina compressor only system and an engine only system.

Other embodiments are within the scope of the following claims.

What is claimed is:
 1. A piston engine, comprising: a plurality ofcylinders, each cylinder having an axis parallel to the axis of theother cylinders, each cylinder having two ends, and each end having aspark plug and inlet and exhaust valves; a distributor for controllingthe timing of the spark plugs and cam shafts for the operation of theinlet and exhaust valves; a plurality of double ended pistons, onedouble ended piston in each cylinder; a transition arm having aconnecting shaft for each double ended piston, each connecting shaftextending into a central opening in each double ended piston; a movableflywheel to adjust the compression ratio of the engine; a drive armconnected to the transition arm and to said flywheel, wherein said drivearm moves into and out of said flywheel when the flywheel is moved toadjust the engine compression; and a drive shaft connected to saidflywheel, the axis of said drive shaft being parallel to the axis ofsaid cylinders.
 2. The engine according to claim 1, wherein said drivearm extends into an opening in said flywheel adjacent to the peripheryof the flywheel.
 3. The engine according to claim 2, wherein said drivearm extends into a sleeve bearing.
 4. The engine according to claim 1,wherein there are four cylinders, including four double ended pistonsforming an eight cylinder engine.
 5. The engine according to claim 1,including a universal joint connecting said transition arm to a support.6. The engine according to claim 1, wherein said transition arm isconnected to a universal joint which permits the transition arm to movewith linear motion produced by the pistons and with a circular motionproduced by the drive arm connected to the flywheel.
 7. The engineaccording to claim 1, including a first pulley connected to a drivegear, a timing belt and a second pulley connected to a distributor. 8.The engine according to claim 7, including an pump driven by said drivegear.
 9. A method for varying the compression ratio of a pistonassembly, comprising: providing a plurality of pistons, a transition armcoupled to a stationary support and to each of the pistons, and arotating member coupled to a drive member of the transition arm andconfigured for sliding movement along the drive member, and sliding therotating member along the drive member to change the compression ratioof the piston assembly.
 10. The method of claim 9 further comprisingdriving the rotating member in rotation to produce linear motion in thepistons.
 11. The method of claim 9 further comprising driving thepistons linearly to produce rotary motion in the rotating member.
 12. Amethod of increasing the efficiency of a piston assembly, comprising:providing a plurality of linearly arranged double ended pistons, atransition arm coupled to each of the double ended pistons atapproximately a center of each of the double ended pistons, and arotating member coupled to a drive member of the transition arm andconfigured for sliding movement along the drive member, and sliding therotating member along the drive member to change the compression ratioand displacement of the double ended piston assembly.
 13. The method ofclaim 12 further comprising driving the rotating member in rotation toproduce linear motion in the pistons.
 14. The method of claim 12 furthercomprising driving the pistons linearly to produce rotary motion in therotating member.
 15. A variable compression piston assembly, comprising:a plurality of pistons, a transition arm coupled to a stationary supportand to each of the pistons, the transition arm including a drive member,and a rotating member coupled to the drive member and configured forsliding movement along the drive member, the rotating member being slidalong the drive member to change the compression ratio of the pistonassembly.
 16. The assembly of claim 15 further comprising a plurality ofcylinders, one piston in each cylinder.
 17. The assembly of claim 16wherein each cylinder has an axis parallel to the axis of each of theother cylinders.
 18. The assembly of claim 16 further comprising a driveshaft connected to the rotating member, an axis of the drive shaft beingparallel to the axes of the cylinders.
 19. The assembly of claim 16wherein each cylinder has two ends, and each end has a spark plug. 20.The assembly of claim 19 further comprising a distributor forcontrolling the timing of the spark plugs.
 21. The assembly of claim 16wherein each cylinder has two ends, and each end has inlet and exhaustvalves.
 22. The assembly of claim 21 further comprising cam shafts foroperation of the inlet and exhaust valves.
 23. The assembly of claim 15wherein the pistons comprise double ended pistons.
 24. The assembly ofclaim 15 wherein the transition arm has connecting shafts coupling thetransition arm to the pistons.
 25. The assembly of claim 24 furthercomprising a plurality of joints, each joint associated with one of thepistons, each joint receiving one of the connecting shafts.
 26. Theassembly of claim 25 wherein the joint is configured to provide degreesof freedom in four directions between the transition arm and arespective piston.
 27. The assembly of claim 25 wherein the jointcomprises: an outer member configured for movement along a first axis,the outer member defining an opening for receiving the connecting shaft,and an inner member mounted within the outer member for rotationrelative to the outer member about a second axis perpendicular to thefirst axis, the inner member defining an opening for receiving theconnecting shaft.
 28. The assembly of claim 27 wherein the inner memberis cylindrical.
 29. The assembly of claim 27 wherein the inner member iscoupled to the outer member for motion along the first axis with theouter member.
 30. The assembly of claim 15 wherein said drive memberextends into an opening in the rotating member adjacent to a peripheryof the rotating member.
 31. The assembly of claim 30 wherein the drivemember extends into a sleeve bearing.
 32. The assembly of claim 15wherein there are four cylinders, including four double ended pistonsforming an eight cylinder engine.
 33. The assembly of claim 15 furthercomprising a universal joint connecting the transition arm to a support.34. The assembly of claim 15 wherein the transition arm is connected toa universal joint which permits the transition arm to move with linearmotion produced by the pistons and with a circular motion produced bythe drive member connected to the rotating member.
 35. The assembly ofclaim 15 further comprising a first pulley connected to a drive gear, atiming belt and a second pulley connected to a distributor.
 36. Theassembly of claim 35 further comprising a pump driven by the drive gear.37. The assembly of claim 15 further comprising means for moving therotating member along the axis of the drive member.
 38. A variablecompression piston assembly, comprising: a plurality of linearlyarranged double ended pistons, a transition arm coupled to each of thedouble ended pistons at approximately a center of each of the doubleended pistons, the transition arm including a drive member,and arotating member coupled to the drive member and configured for slidingmovement along the drive member, the rotating member being slid alongthe drive member to change the compression ratio and displacement of thedouble ended piston assembly.
 39. The assembly of claim 38 furthercomprising a plurality of cylinders, one piston in each cylinder. 40.The assembly of claim 39 wherein each cylinder has an axis parallel tothe axis of each of the other cylinders.
 41. The assembly of claim 40further comprising a drive shaft connected to the rotating member, anaxis of the drive shaft being parallel to the axes of the cylinders. 42.The assembly of claim 39 wherein each cylinder has two ends, and eachend has a spark plug.
 43. The assembly of claim 42 further comprising adistributor for controlling the timing of the spark plugs.
 44. Theassembly of claim 39 wherein each cylinder has two ends, and each endhas inlet and exhaust valves.
 45. The assembly of claim 44 furthercomprising cam shafts for operation of the inlet and exhaust valves. 46.The assembly of claim 38 wherein the pistons comprise double endedpistons.
 47. The assembly of claim 38 wherein the transition arm hasconnecting shafts coupling the transition arm to the pistons.
 48. Theassembly of claim 47 further comprising a plurality of joints, eachjoint associated with one of the pistons, each joint receiving one ofthe connecting shafts.
 49. The assembly of claim 48 wherein the joint isconfigured to provide degrees of freedom in four directions between thetransition arm and a respective piston.
 50. The assembly of claim 48wherein the joint comprises: an outer member configured for movementalong a first axis, the outer member defining an opening for receivingthe connecting shaft, and an inner member mounted within the outermember for rotation relative to the outer member about a second axisperpendicular to the first axis, the inner member defining an openingfor receiving the connecting shaft.
 51. The assembly of claim 50 whereinthe inner member is cylindrical.
 52. The assembly of claim 50 whereinthe inner member is coupled to the outer member for motion along thefirst axis with the outer member.
 53. The assembly of claim 38 whereinsaid drive member extends into an opening in the rotating memberadjacent to a periphery of the rotating member.
 54. The assembly ofclaim 53 wherein the drive member extends into a sleeve bearing.
 55. Theassembly of claim 38 wherein there are four cylinders, including fourdouble ended pistons forming an eight cylinder engine.
 56. The assemblyof claim 38 further comprising a universal joint connecting thetransition arm to a support.
 57. The assembly of claim 38 wherein thetransition arm is connected to a universal joint which permits thetransition arm to move with linear motion produced by the pistons andwith a circular motion produced by the drive member connected to therotating member.
 58. The assembly of claim 38 further comprising a firstpulley connected to a drive gear, a timing belt and a second pulleyconnected to a distributor.
 59. The assembly of claim 58 furthercomprising a pump driven by the drive gear.
 60. The assembly of claim 38further comprising means for moving the rotating member along the axisof the drive member.
 61. A method for varying the compression ratio of apiston assembly, comprising: providing a plurality of pistons, atransition arm coupled to each of the pistons, and a rotating membercoupled to a drive member of the transition arm and mounted for pivotingmovement to slide along an axis of the drive member, and pivoting therotating member to change the compression ratio of the piston assembly.62. A method of increasing the efficiency of a piston assembly,comprising: providing a plurality of double ended pistons, a transitionarm coupled to each of the double ended pistons at approximately acenter of each of the double ended pistons, and a rotating membercoupled to a drive member of the transition arm and mounted for pivotingmovement to slide along an axis of the drive member, and pivoting therotating member to change the compression ratio of the double endedpiston assembly.
 63. A variable compression piston assembly, comprising:a plurality of pistons, a transition arm coupled to each of the pistons,the transition arm including a drive member, and a rotating membercoupled to the drive member and mounted for pivoting movement to slidealong an axis of the drive member, wherein movement of the rotatingmember relative to the drive member changes the compression ratio of thepiston assembly.
 64. The assembly of claim 63 wherein each of thepistons comprises a double ended piston.
 65. The assembly of claim 64wherein the transition arm is coupled to each of the double endedpistons at approximately a center of each double ended piston.
 66. Theassembly of claim 63 wherein the plurality of pistons comprises twopistons and the axis of rotation of the rotating member and axes of thetwo pistons lie on a common plane.
 67. The assembly of claim 66 whereineach of the pistons comprises a double ended piston.
 68. The assembly ofclaim 63 wherein the rotating member comprises a flywheel.
 69. Theassembly of claim 63 further comprising a counterweight mounted to therotating member.
 70. The assembly of claim 63 further comprising a maindrive shaft the rotating member being pivotably mounted to the maindrive shaft.
 71. The assembly of claim 70 wherein an axis of the maindrive shaft is parallel to an axis of each of the pistons.
 72. Theassembly of claim 63 further comprising a movable pressure plate incontact with a peripheral region of the rotating member.
 73. Theassembly of claim 72 further comprising a roller interfacing thepressure plate and the rotating member.
 74. The assembly of claim 72further comprising a piston for biasing the rotating member into contactwith the pressure plate.
 75. The assembly of claim 63 wherein the drivemember extends into an opening in the rotatable member adjacent to aperiphery of the rotatable member.
 76. The assembly of claim 75 whereinthe drive arm extends into a pivot pin located in the rotatable member.77. The assembly of claim 63 further including a universal jointconnecting the transition arm to a support.
 78. The assembly of claim 63further comprising an intake valve.
 79. The assembly of claim 63 furthercomprising an exhaust valve.
 80. The assembly of claim 63 furthercomprising spark plugs.
 81. The assembly of claim 63 comprising anengine.
 82. The assembly of claim 63 comprising a pump.
 83. The assemblyof claim 63 comprising a compressor.